Double offset ball member usable in ball valves and other flow control applications

ABSTRACT

Ball valves and ball valve components usable to control the flow of fluids and methods for manufacturing said ball valve components. Ball valves include a ball member comprising two curved segments of like shape and size, which are integrally joined and disposed symmetrically to one another relative to the axis of rotation of the ball member. A bore extends through the joined first and the second curved segments, wherein the first end of the bore is located on the first curved segment and the second end of the bore is located on the second curved segment. Each curved segment is disposed symmetrically to one another, relative to the axis of rotation. The area of separation, between the curved segments, defines shoulders of like configuration, wherein each shoulder is located symmetrically with respect to the other relative to the ball member&#39;s axis of rotation.

FIELD

Embodiments usable within the scope of the present disclosure relate,generally, to ball valves and other valves usable to control the flow offluids, and more particularly, but not by way of limitation, to a ballmember configuration having a variable radius, which results in avariable force being exerted against the valve seats as the ball memberis turned between the open and closed positions, thereby changing thesealing pressure between the ball member and the valve seats andincreasing the life of the seals in the valve seats.

BACKGROUND

Flow control valves, such as ball valves, are well known in the art andcommonly comprise a valve body or housing having an interior cavity anda pair of fluid flow channels extending through the housing. A ballmember is located within the cavity and is provided with an axialthroughbore, which is selectively aligned with, or disposed transverseto, the fluid channels in the housing, by rotating the ball member aboutan axis of rotation to control the flow of fluid through the fluidchannels. A pair of annular seats are located between the ball memberand the internal wall of the housing and are positioned about thethroughbore and the fluid channels to prevent fluids from leaking intothe interior cavity of the valve.

In valve arrangements of the aforementioned type, seat life and fluidleakage has been a reoccurring problem. Since the ball member isconstantly in sealing engagement with the seats, compressing them inboth the open and closed valve positions, the seats tend to wear outafter a period of time and must be replaced. The problem is particularlymanifested when the valve is used to control flow of an abrasive fluid,when the fluid has a relatively high pressure, and/or when the valve isused under service conditions which require that the valve be rapidlycycled between open and closed positions. The same problem is present tosome degree in all types of ball valves in the course of fluid flowapplications. When the seats have become worn, they are otherwise nolonger capable of performing their intended sealing function and must bereplaced to eliminate consequent leakage of fluid between the housingand the ball member. Replacement of the seats requires that the valve betaken out of service and new seals or seats be installed.

In an effort to deal with the foregoing problems, valve arrangementshave been designed that reduce seat loading when the valve is in itsopen position. For example, one ball valve design includes a split ball,wherein a cam, which rides within a split at the bottom of the ball,spreads the ball to form a tighter seal with the valve seats, as theball is rotated to its closed position. Other designs utilize plugs orball segments, which seal against a single seat in the housing, andwhich are mounted eccentrically on an actuator shaft or a stem, so thatthe plug is moved into forcible contact with the seat in the closedposition of the valve. Moving the valve to the open position moves theplug away from the seat, allowing fluid to flow through the valve.

Valves employing the split ball design or eccentrically offset plugsare, however, relatively complicated and expensive to manufacture andmaintain. Eccentrically mounted plugs also suffer from otherdisadvantages, since they involve an asymmetrical or unbalanced design.Specifically, eccentrically mounted plug valves are prone to leakingproblems arising from rapid internal component wear, resulting from lackof structural support to counter forces created by high fluid pressures.

Therefore, there is a need for a fluid flow control valve that obviatesall the above problems by providing a novel ball member having asymmetrical and balanced design, improving the internal structuralsupport to counter forces created by high fluid pressures.

There is also a need for a ball member comprising an outer surfacehaving a gradually increasing radius with respect to the axis ofrotation. As the ball member rotates from the open valve position to theclosed valve position, the outer surfaces gradually seal against a pairof associated upstream and downstream valve seats, to achieve maximumseal loading at the full closed valve position.

There is also a need for an improved ball member configured for use withconventional valve housing and seats, while improving valve life andsealing performance of the valve.

The present invention meets all of these and other needs.

SUMMARY

Embodiments usable within the scope of the present disclosure relate,generally, to flow control valves, components for controlling the flowof fluids through said valves, and methods of manufacturing saidcomponents.

An embodiment includes a ball member usable in a ball valve, the ballmember comprising a first round segment, a second round segment, whereinthe round segments are offset from one another and integrally joinedsymmetrically to one another relative to an axis of rotation of the ballmember. The ball member has a progressively changing radius with respectthe axis of rotation and a bore extending therethrough transverse to theaxis of rotation, wherein the bore has a longitudinal axis. Duringoperation, the ball valve is opened and closed to fluid flow by rotatingthe ball member about the axis of rotation, wherein the rotation of theball member progressively changes force of contact between the ballmember and a ball valve seat. The first round segment can comprise afirst curved surface having a first concave edge and a first convexedge, wherein the second round segment can comprise a second curvedsurface having a second concave edge and a second convex edge.

In an embodiment, the first and second round segments are offset fromone another along the longitudinal axis of the bore. In anotherembodiment, the first round segment comprises a first center point,wherein the second round segment comprises a second center point, andwherein the first center point and the second center point are locatedon opposite sides of the axis of rotation

The ball member can also comprise a first protruding member extendingfrom the first and the second round segments along the axis of rotationand a second protruding member extending from the first and the secondround segments along the axis of rotation opposite the first protrudingmember, wherein the first protruding member and the second protrudingmember can be integrally formed with the ball member.

An embodiment of the ball member can also comprise a first shoulderdefined by a first surface area located between the first and secondround segments, wherein the first round segment extends past the secondround segment and a second shoulder defined by a second surface arealocated between the first and second round segments, wherein the secondround segment extends past the first round segment, wherein the borecomprises a first opening and a second opening, wherein the firstshoulder encircles part of the first opening of the bore, and whereinthe second shoulder encircles part of the second opening of the bore.

An embodiment can also comprise a first border located between the firstand second round segments and a second border located between the firstand second round segments opposite the first border, wherein the firstand second borders are located on the surface of the ball member,wherein the first and second borders are oriented perpendicular to thelongitudinal axis of the bore.

In addition, embodiments usable within the scope of the presentdisclosure relate to a method for manufacturing a ball member, one suchmethod comprises the steps of forming a first spherical portion of theball member by moving a cutting tool toward a workpiece along an axis ofthe cutting tool and by rotating the workpiece about 180 degrees aboutan axis of rotation oriented generally perpendicular to the axis of thecutting tool. Forming a second spherical portion of the ball membercomprises moving a cutting tool toward the workpiece along the axis ofthe cutting tool, rotating the workpiece about 180 degrees about theaxis of rotation oriented generally perpendicular to the axis of thecutting tool, and machining a bore through the first and second curvedportions transverse to the axis of rotation. The steps comprisingforming the first and second portions can be performed simultaneously.

Alternate embodiment of the process can include the step of moving thecutting tool generally perpendicular to both the axis of the cuttingtool and the axis of rotation away from a point of intercept of saidaxes for about a first 90 degrees of rotation of the workpiece andtowards the point of intercept of said axes for about a second 90degrees of rotation of the workpiece. An embodiment can also includesteps of forming a variable radius of the ball member relative to theaxis of rotation.

The method for manufacturing a ball member can also include the steps ofmachining the workpiece to form a first cylindrical protrusion along theaxis of rotation and machining the workpiece to form a secondcylindrical protrusion along the axis of rotation opposite the firstcylindrical protrusion.

In addition, embodiments usable within the scope of the presentdisclosure relate to other embodiments of a ball member usable in a ballvalve, the ball member comprising a body segment having a generallyrounded shape and an axis of rotation, wherein the body segmentcomprises a bore having a longitudinal axis, wherein the bore extendsthrough the body segment transverse to an axis of rotation, a firstsloped surface, and a second sloped surface. The first and second slopedsurfaces comprise a progressively changing radius with respect to theaxis of rotation, wherein the ball valve is opened and closed to fluidflow by rotating the body segment about the axis of rotation. Each ofthe first and second sloped surfaces may comprise boundaries having aconcave and a convex shape adjacent to an opening of the bore.

An embodiment can further comprise a first protruding member extendingfrom the body segment along the axis of rotation and a second protrudingmember extending from the body segment along the axis of rotation,opposite the first protruding member. The first protruding member andthe second protruding member can be integrally formed with the bodysegment.

In addition, the ball member can comprise a first shoulder defined by anarea located between the first and second sloped surfaces, wherein thefirst sloped surface extends past the second sloped surface and a secondshoulder defined by an area located between the first and second slopedsurfaces, wherein the second sloped surface can extend past the firstsloped surface. The bore can further comprise a first rim and a secondrim, wherein each of the shoulders encircle part of the correspondingrim of the bore.

The ball member can also comprise a first transition area, locatedbetween the first and second sloped surfaces, and a second transitionarea, located between the first and second sloped surfaces opposite thefirst transition area, wherein the first and second transition areas areoriented generally perpendicular relative to the longitudinal axis ofthe bore.

Also, the ball member can further comprise a first transition, locatedbetween the first and second sloped surfaces, and a second transitionlocated between the first and second sloped surfaces opposite the firsttransition area, wherein the first and second transitions are orientedgenerally parallel relative to the first and second rims, respectively.

Lastly, the ball member can comprise a first shoulder defined by an arealocated between the first and second sloped surfaces, wherein the firstsloped surface extends past the second sloped surface and a secondshoulder defined by an area located between the first and second slopedsurfaces, wherein the second sloped surface extends past the firstsloped surface, wherein the first and second shoulders are orientedgenerally parallel relative to each other.

BRIEF DESCRIPTION OF THE DRAWINGS

In the detailed description of various embodiments usable within thescope of the present disclosure, presented below, reference is made tothe accompanying drawings, in which:

FIG. 1 depicts a cross sectional side view of an embodiment of thedevice usable within the scope of the present disclosure, which includesan embodiment of the ball valve in the open valve position.

FIG. 2 depicts a cross sectional front view of an embodiment of thedevice usable within the scope of the present disclosure, which includesan embodiment of the ball valve in the open valve position.

FIG. 3A depicts a cross sectional top view of an embodiment of thedevice usable within the scope of the present disclosure, which includesan embodiment of the ball valve in the open valve position.

FIG. 3B depicts a cross sectional top view of an embodiment of thedevice usable within the scope of the present disclosure, which includesan embodiment of the ball valve in the closed valve position.

FIG. 4 depicts a cross sectional close-up view of an embodiment of thedevice usable within the scope of the present disclosure, which includesan embodiment of the ball valve seats in the open valve position.

FIG. 5A depicts an isometric view of an embodiment of the device usablewithin the scope of the present disclosure, which includes an embodimentof the ball member.

FIG. 5B depicts an isometric view of an embodiment of the device usablewithin the scope of the present disclosure, which includes an embodimentof the ball member.

FIG. 6A depicts a top view of an embodiment of the device usable withinthe scope of the present disclosure, which includes an embodiment of theball member.

FIG. 6B depicts a top view of an embodiment of the device usable withinthe scope of the present disclosure, which includes an embodiment of theball member.

FIG. 7 depicts an isometric view of an embodiment of the device usablewithin the scope of the present disclosure, which includes a fly cutterand an embodiment of the ball member.

DETAILED DESCRIPTION OF THE EMBODIMENTS

Before describing selected embodiments of the present disclosure indetail, it is to be understood that the present invention is not limitedto the particular embodiments described herein. The disclosure anddescription herein is illustrative and explanatory of one or moreembodiments and variations thereof, and it will be appreciated by thoseskilled in the art that various changes in the design, organization,order of operation, means of operation, equipment structures andlocation, methodology, and use of mechanical equivalents can be madewithout departing from the scope of the invention.

As well, it should be understood that the drawings are intended toillustrate and plainly disclose selected embodiments to one of skill inthe art, but are not intended to be manufacturing level drawings orrenditions of final products and can include simplified conceptual viewsas desired for easier and quicker understanding or explanation. As well,the relative size and arrangement of the components can differ from thatshown and still operate within the scope of the invention. It shouldalso be noted that like numbers appearing throughout the variousembodiments and/or figures represent like components.

Moreover, it should also be understood that various directions such as“upper,” “lower,” “bottom,” “top,” “left,” “right,” and so forth aremade only with respect to explanation in conjunction with the drawings,and that the components can be oriented differently, for instance,during transportation and manufacturing as well as operation. Becausemany varying and different embodiments can be made within the scope ofthe concepts herein taught, and because many modifications can be madein the embodiments described herein, it is to be understood that thedetails herein are to be interpreted as illustrative and non-limiting.

Embodiments usable within the scope of the present disclosure relate,generally, to ball valves and other valves used to control the flow offluids, and more particularly, but not by way of limitation, to a ballmember configuration having a variable radius with respect to its axisof rotation, which results in a variable force being exerted against thevalve seats as the ball member is turned between the open and closedpositions, thereby changing the sealing pressure between the ball memberand the valve seats and increasing the life of the valve seats.

Referring now to FIGS. 1, 2, 3A, and 3B, an embodiment of a fluid ballvalve in accordance with the present invention is generally depicted.The ball valve (10) comprises, in general, a valve body or a housing(20), a top cover or a bonnet (22), a rotating actuation member or astem (40), seats (30 a, 30 b), and a generally spherical shaped flowrestricting member or a ball member (50).

The housing (20) can be arranged to have any of several well-knownexternal configurations and as depicted in FIGS. 1, 2, 3A, and 3B. Atthe center of the housing (20) is a generally spherical chamber, calleda housing cavity (24), which encompasses the ball member (50). Thehousing further comprises a pair of fluid channels (21 a, 21 b)extending through the housing, on opposite sides of the central cavity(24). The fluid channels (21 a, 21 b) define an axial fluid passagewaythrough the housing (20), enabling fluid transfer between external fluidconduits (not shown) or other equipment connected to the valve (10). Thefluid channels (21 a, 21 b) can be configured to terminate with spacedflanges (23 a, 23 b), as depicted in FIGS. 1, 3A, and 3B, each of whichcan be connected to external fluid conduits (not shown) or otherequipment, by bolts or by other means, such as threaded connectors (notshown). While the housing (20) need not be symmetrical as depicted, itis often desirable that the valve permits complete symmetry inorientation of installation. Thus, a ball valve (10) can be connectedinto a fluid system without regard to which flange (23 a, 23 b) is beingconnected to the pressure side of the fluid line.

As depicted in the embodiment of FIGS. 1 and 2, enclosing the topopening in the valve cavity is a bonnet (22), shown as a generally roundand symmetrical plate member. The center of the bonnet (22) contains anaperture (41) of sufficient diameter to accommodate a valve actuatingmember, or a stem (40), extending therethrough in a perpendicularorientation relative to the top surface of the bonnet (22). The centralaperture (41) contains a counterbore section, defining an uppercylindrical cavity (42), formed coaxially with the aperture (41) andlocated at the lower end of the aperture (41). The upper cylindricalcavity (42) structurally retains and supports portions of the stem (40)and the ball member (50). The upper portion of the valve stem (40)extends beyond the aperture (41) and terminates with an upper stem drivemember (43), which is configured for connection with a valve actuator(not shown). The stem (40) can be rotated by means of a handle (notshown) attached to the upper stem drive member (43), allowing selectiverotation of the ball member (50) between the open valve position shownin FIGS. 1, 2, and 3A, and the closed valve position shown in FIG. 3B.The actuation of the stem (40) can also be automated, whereby therotation is performed by a fluid powered or electrical rotary actuator(not shown) attached thereto.

The lower portion of the valve stem terminates with an annular supportring (44), which extends radially from the lower portion of the valvestem (40). The annular support ring (44) engages the lateral surface ofthe upper cavity (42) to maintain the coaxial alignment between thevalve stem (40) and the bonnet aperture (41). The annular support ring(44) also engages the upper surface of the upper cavity (42) to retainthe valve stem (40) within the bonnet aperture (41) and to maintainengagement with the ball member (50). The upper cavity (42) isconfigured to receive both the support ring (44) as well as the uppertrunnion (56). As in the depicted embodiment, the upper cavity (42) canhave varying diameters in order to accommodate a support ring (44) andan upper trunnion (56) having different diameters.

As further depicted in FIGS. 1 and 2, sealing members (45) occupy theannular space between the stem (40) and the bonnet (22). These annularsealing members (45) perform the usual function of packing the stem (40)and can be fabricated from any known sealing or packing materials andconfigured in any manner known in the art, including, but limited to,elastomer O-ring seals, cup seals, polymer seals, composite seals, andmetal seals.

The top portion of the housing (20) terminates with a ridge (25), whichdefines a valve cavity opening (26). The ridge (25) comprises theconnection means for mounting of the bonnet (22) to the housing (20) ina secured and sealed relation. FIGS. 1 and 2 depict the means forconnection to be in the form of a flange connection, securing the bonnet(22) to the housing (20) by means of a plurality of retainer threadedstud and nut assemblies (27). Although the figures depict oneembodiment, it is not intended to limit the scope of the presentinvention to a bolted bonnet (22) construction. A number of bonnetconnection systems (not shown) are commercially available at the presenttime and can be employed to secure a bonnet member, in sealed andpositively retained assembly, with a valve body.

Referring again to FIGS. 1, 3A, and 3B, the embodiments depicted show apair of annular sealing instruments, called seats (30 a, 30 b), whichare supported against the housing (20) and located about the fluid flowchannels (21 a, 21 b). Located at the inside terminus of each fluidchannel (21 a, 21 b) is a seat shoulder (28 a, 28 b) usable to supportthe seats (30 a, 30 b) in position. Each seat shoulder (28 a, 28 b) canbe shaped and proportioned to retain the corresponding seat (30 a, 30 b)in place during operation, preventing the seats from shifting whenengaged with the ball member (50). The seats (30 a, 30 b), usable withinthe disclosed ball valve (10), can be of any type known in the industry.Among the seat configurations usable with the disclosed ball member (50)are double-block and bleed (DBB) and double-isolation and bleed (DIB)seat types, such as defined by API 6D/ISO 14313 design specifications.

FIGS. 1, 3A, 3B, and 4 depict DIB seats (30 a, 30 b) as one embodimentof the seats (30 a, 30 b) usable with the currently disclosed ballmember (50). DBB valves typically contain two unidirectional seats (notshown). The unidirectional seats, when energized, isolate the pressurein the flow channels (21 a, 21 b) from the housing cavity (24) betweenthe seats. If pressure is reversed, the seats are urged away from theball member (50) and allow pressure to relieve from the housing cavity(24) to the flow channels (21 a, 21 b). This is a desirable function,particularly in liquid service. In the case where the valve housingcavity (24) is filled with liquid and heated due to process flow orexternal sources, pressure can build due to thermal expansion of theliquid in the housing cavity (24). Without the self-relievingunidirectional seats, this could lead to over-pressure in the valvecavity (24) resulting in leakage or rupture. DIB valves include one ortwo bidirectional seats (30 a, 30 b), as depicted in FIGS. 1, 3A, 3B,and 4. When two bidirectional seats (30 a, 30 b) are used, the valveprovides double isolation from pressure at either flow channel (21 a, 21b). This configuration has one operational drawback in that it cannotrelieve pressure in the housing cavity (24) past the seats (30 a, 30 b).An external relief piping system (not shown) must be used to allow anypressure build-up in the housing cavity (24).

The action of the seats is determined by the pressure differentials thatact on the seats. For the unidirectional seat (not shown), upstreampressure urges the seat against the ball member (50) and creates a sealbetween the seat and the ball member (50). Pressure in the housingcavity (24), on the other hand, urges the seat away from the ball member(50), breaking the seal between the ball member (50) and the seat,thereby relieving pressure within the housing cavity (24). Conversely,the bidirectional seats (30 a, 30 b) are urged against the ball member(50) by pressure regardless of the location of the pressure source,whether it's the fluid channel (21 a, 21 b) or the housing cavity (24).The DIB feature provides a second fluid flow barrier, such that whilepiping is removed downstream (as in a repair situation), the housingcavity (24) can be monitored for upstream seat leakage. The downstreamseat provides the second barrier in the event the upstream seat beginsleaking during the maintenance or repair.

FIG. 4 depicts a close-up view of one embodiment of a DIB seat (30 a)usable within the scope of the current disclosure. The first seat (30 a)comprises a plurality of seat segments (31, 32, 33) and a plurality ofsealing elements (35, 36, 37), assembled to form the first seat (30 a).The rear seat segment (32) is positioned against the first housingshoulder (28 a) and encompasses the first sealing element (37) (e.g. anO-ring), which seals against the first shoulder (28 a), limiting leakageadjacent to the shoulder. The interior seat segment (31) is alsopositioned against the first housing shoulder (28 a), but is longer andextends past the rear seat segment (32). A second sealing element (36)is located between the rear seat segment (32) and the interior seatsegment (31), limiting fluid leakage therebetween. An exterior seatsegment (33) is located around the rear and interior seat segments (32,31), with a third sealing element (35), called an insert, locatedbetween the exterior seat segment (33) and the ball member (50),limiting fluid leakage adjacent to the ball member (50).

The embodiment of the first seat (30 a) depicted in FIG. 4, is anexample of a floating and expandable seat usable with the valve (10) andthe ball member (50) of the current disclosure. A floating andexpandable seat design allows a uniform sealing action against surfaces,which may be unevenly placed against the seat. For example, in theclosed ball valve position, one side of the ball member (50) can bepositioned closer to one side of the housing shoulder (28 a), resultingin greater compression of one side of the seat (30 a). The disclosedfloating and expandable seat design allows the seat (30 a) to movetowards or away, as well as sideways, from the ball member (50) andtherefore adjust to uneven contact with the ball member (50), resultingin a generally uniform seat loading by the ball member (50). Althoughone embodiment of a floating seat is depicted in FIG. 4, any floatingand expandable seat design known in the industry may be used with theball valve (10) and the ball member (50) disclosed in the currentapplication.

Also depicted in FIG. 4 is a first retainer (34 a), which maintains thefirst seat (30 a) in a generally constant position between the firstshoulder (28 a) and the ball member (50). As further depicted in FIG. 1,the first retainer (34 a) can be held in position by connecting it to alower portion of the bonnet (22), by use of any known means, such asthreaded bolts, for example.

Located within the housing cavity (24) is a fluid flow obstruction,called the ball member (50). As depicted in FIGS. 5A and 5B, the ballmember (50) has a generally spherical or round shape comprising twopartially spherical members, called spherical segments (51 a, 51 b), athroughbore (55), an upper trunnion (56), and a lower trunnion (57). Theball member (50) is adapted to be rotated about its axis of symmetry(X), which runs vertically through the center of the upper and lowertrunnions (56, 57). The throughbore (55) extends transversely throughthe ball member (50) and functions as a fluid passageway, when each endor rim (66 a, 66 b) of the throughbore (55) is aligned with each fluidchannel (21 a, 21 b), as depicted in FIG. 1. Therefore, the ball member(50) allows communication between the fluid channels (21 a, 21 b) whenactuated to the open position and disconnects the fluid channels (21 a,21 b) when actuated to the closed position, as in a typical ball valvearrangement.

Referring again to FIGS. 1, 2, 3A, and 3B, depicting one embodiment of afluid flow control valve. The figures are not intended to limit thescope of the present invention to that construction as other designs arecommercially available at the present time and can be employed withoutdeparting from the scope of the disclosed invention. Specifically, FIG.1 depicts a ball valve embodiment comprising a throughbore (55) andfluid channels (21 a, 21 b) having a coaxial configuration; however,these fluid channels (21 a, 21 b) can be offset or oriented at arelative angle therebetween and/or in relation to the throughbore (55).Furthermore, the ball member (50) according to the present disclosurecan also comprise a full port or restricted port design. Therefore, thediameter of the throughbore (55) depicted can be equal to, smaller than,or greater than the diameter of the fluid channels (21 a, 21 b).

FIGS. 1 and 2 also depict a ball member (50) having upper and lowertrunnions (56, 57), which function as mounting and pivoting points forthe ball member (50). As the ball member (50) is actuated between theopen and closed positions, it rotates within a cylindrical cavity (42)at its upper end and about a cylindrical protrusion (29) at its lowerend. As stated above, the upper cylindrical cavity (42) is fashioned asa counterbore, located at the lower portion of the bonnet aperture (41).The upper cylindrical cavity (42) receives the upper trunnion (56),while the cylindrical protrusion (29) extends upwardly from the housing(20) into the housing cavity (24), mating within a lower cylindricalcavity (58) in the lower trunnion (57). In the depicted embodiment, theupper trunnion (56) comprises two sections, an upper section, which isinserted into the upper cylindrical cavity (42) as described above, andthe lower section, which comprises an outside diameter that is largerthan the upper cylindrical cavity (42). The lower section of the uppertrunnion contacts the bottom surface of the bonnet (22) to retain theball member (50) in proper vertical position within the housing cavity(24) during operation. The upper and the lower trunnions (56, 57), theupper cylindrical cavity (42), and the cylindrical protrusion (29) arearranged coaxially, resulting in the ball member having an axis ofrotation (X) located through the center of the trunnions (56, 57).

FIGS. 1, 2, 5A, and 5B depict upper and lower trunnions (56, 57)integrally formed with the spherical segments (51 a, 51 b) locatedtherebetween. Such integral construction can be achieved through severaltechniques known in the art, such as, for example, casting the entireball member (50) as a single piece or by using a milling machine to cutthe entire ball member (50) from a single workpiece. Manufacturingprocesses usable to construct the ball member of the current disclosureare described in additional detail below.

In addition to supporting the ball member (50), the upper trunnion (56)also contains a cavity, or a stem receptacle (59), designed to mate withthe stem (40), thereby enabling actuation of the ball member (50). Thebottom portion of the valve stem (40), called the drive member (46),projects downwardly and engages within the stem receptacle (59). Thestem receptacle (59) has a generally rectangular shape configured toreceive the drive member (46). The stem receptacle (59) defines a stemconnection, which can be in the form of a depression or receptacle orcan have any other geometric form that compliments the drive member (46)and permits a non-rotatable relationship to be established between theball member (50) and the stem (40), and can have other suitable geometrywithin the scope of the present invention. In an alternate embodiment,ball member (50) can be provided with a protruding member thatestablishes non-rotatable driving relation with the valve stem (40),which can be provided with a depression or a receptacle.

In addition to providing the pivoting points for the ball member (50),the upper and lower trunnions (56, 57), the upper cylindrical cavity(42), and the cylindrical protrusion (29) provide the ball member (50)with mounting surfaces, giving the ball member (50) structural supportto withstand high fluid pressures, without resulting in fluid leakage orinternal damage. During operation, especially in the closed valveposition, the surface of the ball member (50) can be exposed to highfluid pressures. These pressures can generate large forces on the ballmember (50), resulting in significant internal stresses being exertedupon its support structure. Certain valve designs, such as a floatingball design (not shown), can provide insufficient structural support,resulting in the ball member being shifted, causing fluid leaks into thevalve cavity or the outlet port. Excessive shifting of the ball membercan also result in damage to the trunnions, the stem, and internalseals. The trunnions (56, 57), the upper cylindrical cavity (42), andthe lower cylindrical protrusion (29), as depicted in FIGS. 1 and 2,provide internal support for the ball member (50), maintaining it alongthe axis of rotation (X) and preventing excessive undesired movement ofthe ball member (50).

Although, in the embodiment depicted in FIGS. 1 and 2, the bottomtrunnion (57) of the ball member (50) contains a bottom cylindricalcavity (58) for allowing the ball member (50) to rotate about acylindrical protrusion (29) in the housing (20), other trunnion designscan be incorporated. For example, in one alternate embodiment (notshown), the lower trunnion does not contain a cavity, but comprises asolid cylindrical protrusion that sits within a cylindrical cavityformed within the lower internal surface of the housing. In thisconfiguration, the lower trunnion is engaged within the cylindricalcavity, allowing the ball member to rotate about the axis of rotationwhile providing structural support to the ball member.

As previously stated and depicted in embodiments of FIGS. 5A and 5B, theball member (50), in accordance with the present disclosure, furthercomprises two spherical segments (51 a, 51 b). These spherical segments(51 a, 51 b) comprise partial spheres of like shape and size, which areoffset and integrally joined together, and disposed symmetrically to oneanother relative to the axis of rotation (X). A bore (55) extendsthrough the joined first and the second spherical portions, wherein thefirst terminus of the throughbore (55) is located on the first sphericalsegment (51 a) and the second terminus of the throughbore (55) islocated on the second spherical segment (51 b). The throughbore (55) isoriented generally perpendicular to the axis of rotation. However, inalternate embodiments, the throughbore (55) can be oriented in atraverse manner relative to the axis of rotation.

Furthermore, in the embodiments of the ball member (50) shown in FIG.6A, depicting the top view of the ball member (50), each sphericalsegment (51 a, 51 b) comprises a center of sphere, called an offsetpoint (58 a, 58 b), as each center of sphere is offset from the ballmember's axis of rotation (X). Each offset point (58 a, 58 b) is locatedon either side of axis of rotation (X) along the longitudinal axis (Z)of the throughbore (55). Each spherical segment (51 a, 51 b) exhibits aradius (61 a, 61 b) with respect to its respective offset point (58 a,58 b), located along the longitudinal axis (Z) of the throughbore (55)at a specific offset distance (62 a, 62 b) from the axis of rotation(X). Due to the offset distances (62 a, 62 b), the two offset points (58a, 58 b), marking the centers of each spherical segment (51 a, 51 b),are shifted from each other by a distance comprising the sum of thefirst and second offset distances. Although FIG. 6A depicts anembodiment of the ball member (50) having offset points (58 a, 58 b)located along the longitudinal axis (Z), alternate embodiments of theball member (50) can comprise offset points being located in variouspoints along the Y-Z plane. The specific location of the offset points(58 a, 58 b) define the orientation of each spherical segment (51 a, 51b) relative to the other, which affects the height of the shoulders (54a, 54 b) and the characteristics of the radius (65 a, 65 b, see FIG. 6B)of the ball member (50) with respect to the axis of rotation (X).

As further depicted in FIG. 6A, because the two spherical segments (51a, 51 b) are offset, there exist two areas of separation, calledshoulders (54 a, 54 b), located between the spherical segments (51 a, 51b) at the points where one spherical segment transitions to the other.The two shoulders (54 a, 54 b) are of like configuration, located onopposite sides of the ball member (50), wherein each shoulder is locatedsymmetrically, with respect to the other, relative to the ball's axis ofrotation (X). In the depicted embodiment, the shoulders (54 a, 54 b) areoriented generally perpendicular to the longitudinal axis (Z) of thethroughbore. In the same embodiment, the shoulders (54 a, 54 b) can beoriented generally parallel with the rims (66 a, 66 b) of thethroughbore (55).

Referring now to FIGS. 6A and 6B, an embodiment of the ball member (50)in accordance with the present disclosure is depicted. Although eachspherical segment (51 a, 51 b) has a radius (61 a, 61 b) with respect toits offset point (58 a, 58 b), and exhibits a progressively increasing(or decreasing depending on direction) radius, called variable radius(65 a, 65 b), with respect to the axis of rotation (X), whereby themaximum radius is located at the top of the shoulder (54 a, 54 b) andthe minimum radius is located at the bottom of the shoulder (54 a, 54b). The surface area adjacent to the top of the shoulder (54 a, 54 b) iscalled the high surface area (52 a, 52 b), and the surface area adjacentto the bottom of the shoulder (54 a, 54 b) is called the low surfacearea (53 a, 53 b). As depicted in the embodiment in FIGS. 6A and 6B, thethroughbore (55) penetrates the ball member through the low surface area(53 a, 53 b) of each spherical segment (51 a, 51 b). As a result, eachlow surface area (53 a, 53 b) of the ball member is truncated along thelongitudinal axis (Z) of the throughbore (55).

As depicted in FIGS. 5A and 5B, the shape of the surface area of eachspherical segment (51 a, 51 b) is further defined by the upper and lowertrunnions (56, 57) extending from the ball member (50), having thespherical segments (51 a, 51 b) located therebetween. Specifically, theupper and lower boundaries of the surface areas of each sphericalsegment (51 a, 51 b) are defined by the trunnions (56, 57), whereby theupper and lower boundaries (i.e., edges) of the surface area of eachspherical segment (51 a, 51 b) curve about the upper and lowertrunnions. The lateral boundaries of the surface area of each sphericalsegment (51 a, 51 b), defined by the shoulders (54 a, 54 b), curveadjacent to the first and second rim (66 a, 66 b) of the throughbore(55). Specifically, the first lateral outwardly curving boundary (notshown) of the surface area of the first spherical segment (51 a) curvesoutwardly (i.e., a convex boundary), around the far side of the firstrim (66 a), thereby encompassing the first rim (66 a), while theopposite lateral inwardly curving boundary (68 a) (i.e., a concaveboundary) into the surface area, adjacent the near side of the secondrim (66 b), thereby excluding the second rim (66 b). The shape of thespherical area of the second spherical segment (51 b) has a similarshape, comprising an outwardly curving boundary (67 b) (i.e., convexboundary) encompassing the second rim (66 b) and an inwardly curvingboundary (not shown) (i.e., concave boundary) excluding the first rim(66 a). Therefore, if the surface area of each spherical segment (51 a,51 b) was unrolled or its curvature about the axis of rotation (X) wasstraightened, the surface area of each spherical segment (51 a, 51 b)would have an elongated lune-like shape, wherein the concave and convexboundaries are separated by an additional area therebetween.

Referring now to FIG. 6B, the outer point (63 a, 63 b) of each shoulderinitiates at a predetermined angle (64 a, 64 b) relative to thelongitudinal axis (Z) of the throughbore (55), wherein each shoulder (54a, 54 b) outlines a throughbore opening along a plane perpendicular tothe throughbore axis (Z). In the depicted embodiment, the outer point(63 a, 63 b) of each shoulder (54 a, 54 b) is located at an angle (64 a,64 b) relative to the axis (Z) of the throughbore (55). The height ofeach shoulder (54 a, 54 b) can be defined as the difference between themaximum and minimum radius (56 a, 56 b) of the ball member (50) adjacentto the shoulder (54 a, 54 b). The relative dimensions of the shoulders(54 a, 54 b) and the offset distances (62 a, 62 b), as depicted in FIG.6A, are exaggerated for clarity, and in actual embodiments the height ofeach shoulder is very small. For example, in one embodiment, the ballmember can have a sphere radius (61 a, 61 b) of 3.500 inches, an offsetdistance (62 a, 62 b) of 0.030 inches, a shoulder (54 a, 54 b) height of0.060 inches, and the shoulder angle (64 a, 64 b) of 37.000 degrees.

Although the two spherical segments (51 a, 51 b) are described as beingseparate and distinct, the ball member (50) has a unitary configuration,wherein the two spherical segments (51 a, 51 b) are integrally formed.The outside surface of each spherical segment (51 a, 51 b) defines asealing surface of the ball member (50), comprising a smooth finish,which enables it to form a fluid seal when compressed against the valveseats (30 a, 30 b) during operation. The spacing of the offset points(58 a, 58 b) relative to the axis of rotation (X) provides the ballmember (50) with eccentric properties. Wherein each spherical segment(51 a, 51 b) comprises a radius (61 a, 61 b) with respect to itscorresponding offset point (58 a, 58 b), each spherical segment (51 a,51 b) can be eccentric with respect to the axis of rotation (X),enabling the ball member (50) to progressively increase contact forceagainst the seats (30 a, 30 b). As the ball member (50) is rotated aboutthe axis of rotation (X), which is traverse or generally perpendicularto the longitudinal axis (Z) of the throughbore (55), each sphericalsegment (51 a, 51 b) contacts a corresponding seat (30 a, 30 b) withprogressively increasing or decreasing force. The operation of the valveis described in more detail below.

While the first and second spherical segments are defined above ascomprising partial spheres of like shape and size, alternate embodimentsexist, wherein each spherical segment comprises a spherical shape or anyother rounded shape that may not be spherical. Specifically, thespherical segments may be generally rounded segments, comprisingthree-dimensional curved surfaces, having circular, elliptical, oval,spiral, or other curvatures. Although the generally rounded segments maynot contain singular centers that are offset relative to the axis ofrotation, the segments can be offset from one another and integrallyjoined, having the curved surfaces oriented away from each other. Thegenerally rounded segments can also be disposed symmetrically, to oneanother, with respect to the axis of rotation.

The ball member (50), in accordance with the present disclosure asdescribed above, can be incorporated into valve bodies havingalternative designs and/or standard valve bodies known in the industry.One alternative embodiment (not shown) includes a ball valve, having avalve body comprising a bottom opening, whereby the bottom of the bodyis closed by a flanged cover. The internal surface of the valve bodydefining the valve cavity can comprise cylindrical cavities, asdescribed in the embodiment depicted in FIGS. 1, 2, 3A, and 3B; however,the ball member can be installed in the valve cavity through the bottomopening. The upper trunnion (56) of the ball member can be inserted intoa corresponding upper cylindrical cavity, while the lower trunnion (57)can be supported by a cylindrical protrusion or a bottom cylindricalcavity located within the bottom flange cover. The ball valve canotherwise be configured in the manner described above and depicted inFIGS. 1, 2, 3A, and 3B.

Another alternative ball valve design (not shown) can include a valve,wherein the ball member (50) is disposed between seats in a two-piece ora three-piece ball valve body, which are well known in the industry. Theball member (50) can be installed in the valve cavity through the sideopening in the main body, prior to installation of an end member, whichcan have threaded ports or a flange connection for connecting to themain body. The housing cavity can be designed to accommodate upperand/or lower trunnions (56, 57) by having a cooperative groove on thetop and/or bottom inside surfaces of the valve body defining the cavity.

In another embodiment (not shown), the ball member may not contain theupper and/or the lower trunnions (56, 57), whereby the valve cancomprise a floating ball valve design. The upper end of the ball member(50) of the floating ball valve design can comprise a flush cavity toaccommodate the bottom or the insertable end of the valve stem. In thefloating ball valve, the ball member (50) can be held in place by thesealing elements (i.e. the seats) and the stem. Such floating ball valvedesign is well known in the art. In the floating ball embodiment, theball member can self-centering and is not prone to problems fromtolerance variations as, during operation, the ball member tends to movedownstream slightly, compressing and sealing against the seats.

Embodiments usable within the scope of the present disclosure alsorelate to methods of manufacturing the ball member (50). As describedabove, one manufacturing technique utilizes a milling machine, or anyother similar device, to cut the entire ball member (50) from a singleworkpiece (not shown), wherein the workpiece is typically a solid pieceof material, such as stainless steel, which is machined to form the ballmember (50). The workpiece in the described embodiment comprises thesame X, Y, and Z axes as the ball member (50).

Referring now to FIG. 7, one embodiment of the process of manufacturingthe ball member (50) according to the present disclosure is shown. Thefigure depicts a ball member (50) engaged with a milling machine (notshown) having a fly cutter (70) located above the ball member (50). Thefigure also designates local coordinates X, Y, and Z, relative to theball member (50), and universal coordinates, X1, Y1, and Z1, relative tothe milling machine and fly cutter (70). The local coordinates are fixedwith the ball member (50), wherein the X axis is always aligned with theaxis of rotation (X), the Z axis is always aligned with the longitudinalaxis (Z), and the Y axis is always located perpendicular to the both theX and Z axes. During the manufacturing process, the local coordinates,X, Y, and Z, change directions with respect to the universal coordinatesX1, Y1, and Z1 as the ball member (50) is rotated about the X and X1axes, which are aligned. The universal coordinates remain static,regardless of the movement of the ball member (50).

One embodiment of the manufacturing process incorporates the use of amilling machine having the capacity to rotate the workpiece about the X1axis and move the fly-cutter (70) along the Y1 and Z1 axes. A blankworkpiece is first engaged with a milling machine, having a spindle andtailstock along the X1 axis, which grip the workpiece on opposite sides,along the X axis of the workpiece.

At the initial stages of the manufacturing process, the local anduniversal coordinates have the same origin, with X, Y, and Z coordinatesbeing aligned with the X1, Y1, and Z1, coordinates respectively. Theinitial location of the fly cutter along the local coordinates is (0, 0,Z) and along the universal coordinates is (0, 0, Z1), wherein Z and Z1values are equal.

The first phase of the milling operations comprise descending therotating fly cutter (70) towards the origin along the Z and Z1 axis to avalue that is equal to the sum of the first radius (61 a) and the firstoffset distance (62 a).

The second phase comprises simultaneously: 1) rotating the workpiece, ata constant speed, 180 degrees counter-clockwise, about the X1 axis, 2)further descending the fly cutter towards the origin along the Z1 axis,moving a distance that is equal to the sum of the desired offsetdistances (62 a, 62 b), and 3) moving the fly-cutter along the Y1 axisaway from the origin for the first 90 degrees of rotation and thentowards the origin for the second 90 degrees of rotation, wherein thedistance of each motion is equal to the desired first offset distance(62 a). The above three steps initiate and terminate at the same timeand machine the first spherical segment (51 a). At this point, thesecond spherical segment (51 b) can be machined by repeating the firstand second phases of the milling operations.

The third phase of the milling operations comprise resetting therotating fly-cutter (70) above the ball member (50), opposite thestarting position of the second phase. As the second phase ends on saidopposite side, the fly-cutter can be reset by moving it away from theorigin along the Z and Z1 axis to a value that is equal to the sum ofthe second radius (61 b) and the second offset distance (62 b).

The fourth phase comprises simultaneously: 1) rotating the workpiece, ata constant speed, 180 degrees counter-clockwise, about the X1 axis, 2)descending the fly cutter towards the origin along the Z1 axis, moving adistance that is equal to the sum of the desired offset distances (62 a,62 b), and 3) moving the fly-cutter along the Y1 axis away from theorigin for the first 90 degrees of rotation and then towards the originfor the second 90 degrees of rotation, wherein the distance of eachmotion is equal to the desired second offset distance (62 b). The abovethree steps initiate and terminate at the same time and machine thesecond spherical segment (51 b). Although the method described abovediscloses rotating the workpiece 180 degrees about the X1 axis, otherembodiments of the ball member (50) may require a different method ofmanufacture, for example, that the workpiece be rotated more or lessthan 180 degrees, in order to meet the structural requirements of theball member (50). Similarly, although the method described abovediscloses moving the fly-cutter along the Y1 axis in specific directionsand at specific times during the manufacturing process, in otherembodiments of the manufacturing process, the fly-cutter may move alongthe Y1 axis at different times and different directions, depending onthe structural requirements of the ball member (50).

The throughbore (50) can be created by cutting a bore along the Z axis,using any known means, such as a different fly cutter, a drill, or alathe. The trunnions (56, 57) can also be machined by any known means,such as an appropriately sized fly cutter, a drill, or a lathe. Althoughdescribed last, the throughbore (50) and the trunnions (56, 57) can bemachined either at the beginning or the end of the manufacturing processof the ball member (50).

The ball member (50), as described above, provides operationalimprovements over valves utilizing typical ball members. FIGS. 1, 2, and3A depict the aforementioned ball member (50) in its open position,mounted within the housing cavity (24) formed by the valve housing (20)and the bonnet (22), as described above. The ball member (50) is adaptedto be rotated through about 90 degrees, whereby in the open position,the throughbore (55) can be aligned with said axial flow channels (21 a,21 b), as shown in FIG. 1, and in the closed position, the throughborecan be disposed transverse to the axial flow channels (21 a, 21 b), tocontrol the flow of fluid through the valve housing (20), as shown inFIG. 3B.

A pair of annular seats (30 a, 30 b) are supported by housing shoulders(28 a, 28 b) located about the interior ends of the fluid channels (21a, 21 b), wherein the shoulders (28 a, 28 b) support the seats (30 a, 30b) for engagement with the ball member (50). Due to the configuration ofthe ball member (50), the housing cavity (24), and the seats (30 a, 30b), the ball member (50) engages the seats with a variable force,depending on the angular position of the ball member (50) with respectto the seats (30 a, 30 b). Referring also to FIG. 6B, depicting anembodiment of the ball member (50), as the spherical segments (51 a, 51b) of the ball member comprise variable radii (65 a, 65 b) relative toits axis of rotation (X), the force with which the ball member (50)exerts on the seats (30 a, 30 b) varies with its angular position.Because the low surface areas (53 a, 53 b) surrounding the throughbore(55) have shorter radii (65 a, 65 b), the compressive forces with theseats (30 a, 30 b) are the smallest in the open valve position. As theradius (65 a, 65 b) of the ball member (50) increases while moving awayfrom the throughbore (55), the compressive forces between the ballmember (50) and the seats (30 a, 30 b) increase.

Therefore, as the ball member (50) is rotated toward the closed valveposition, the high surfaces (52 a, 52 b) of the ball member (50) contactadjacent surfaces of the seats (30 a, 30 b) with an increasing force,with maximum seat loading being achieved in the fully closed position ofball member (50). The amount of offset (62 a, 62 b) that is providedbetween the high surface areas (52 a, 52 b) and low surface areas (53 a,53 b) to enable this operation is determined experimentally, and to someextent, can be proportional to the size of the valve (10). As the sizeof the valve (10) increases, the extent to which the seats (30 a, 30 b)deflect increases, therefore the amount of offset (62 a, 62 b) betweeneach spherical segment (51 a, 51 b) and the axis of rotation (X) is alsoincreased.

Although each of the embodiments described above comprises a ball member(50) having offset spherical segments (51 a, 51 b), the ball member hasa symmetrical design, wherein the spherical segments (51 a, 51 b) aresymmetrically positioned about the axis of rotation (X). Furthermore,the ball member (50) is positioned centrally between the two seats (30a, 30 b), resulting in a balanced valve design, wherein the ball member(50) seals against both seats (30 a, 30 b) in the closed valve position.The balanced valve design results in an equal pressure being exertedupon each seat (30 a, 30 b), giving the ball member (50) additionalstructural support against excessive internal strains caused by highfluid pressures. Because of the progressively larger diameter, thetorque required to rotate the ball member (50) steadily increases, oncethe ball member comes into contact with the seats (30 a, 30 b). Sincethe force of contact is low for most of the valve cycle, increasingsignificantly as the ball member (50) reaches the closed valve position,a longer seat life is possible, since compressive and frictional forceson the seats (30 a, 30 b) are reduced as the ball member (50) is rotatedto its open valve position.

In the depicted embodiment of the present disclosure shown in FIG. 1,the seats (30 a, 30 b) and the dimensions of the aforementioned valveelements are so selected that, in the open position of the valve (10),the surfaces of the spherical segments (51 a, 51 b) contact the seats(30 a, 30 b) without causing significant flexure of the seats (30 a, 30b). This arrangement allows for minimal compression and, therefore,decreases wearing action caused by the ball member (50). Furthermore,because the two offset points (58 a, 58 b) are located in-line along thelongitudinal axis (Z) of the throughbore (55), the low surface areas (53a, 53 b), adjacent to the rims (66 a, 66 b) of the throughbore (55),comprise a symmetrical radius with respect to the axis (Z). This designenables the ball member to make even contact with the entire seat (30 a,30 b), resulting in uniform seat loading with the ball member (50).

In the closed valve position, located about 90 degrees from the openvalve position, the two offset points (58 a, 58 b) are located laterallywith respect to the seats (30 a, 30 b), which results in high surfaceareas (52 a, 52 b) having a progressively increasing radius (65 a, 65 b)with respect to the axis of rotation (X). This design can result in anuneven seat (30 a, 30 b) loading, wherein the portion of the seatslocated closest to the shoulder (54 a, 54 b) are compressed more orfurther than the portion located away from the shoulder (54 a, 54 b).Non-uniform compression can be compensated by seats (30 a, 30 b) havingadjustable or floating design, such as disclosed above and depicted inFIG. 4 or in U.S. Patent Application Publication No. 2010/0308247A1,which is incorporated herewith in its entirety.

The ball member (50) disclosed herein can also be used with other seatsknown in the industry, which adjust to a ball member (50) that makesuneven contact with the seats. For example, in another embodiment, theseats can be statically positioned between the housing shoulders (28 a,28 b) and the ball member (50), wherein the elastic and other propertiesof the sealing members allow uneven contact with a ball member (50),while maintaining a leak tight seal. Lastly, as certain embodiments ofthe ball member (50) comprise small offset distances (62 a, 62 b) andsmall shoulder (54 a, 54 b) heights, almost any commercially availableseat will function in conjunction with the ball member (50) of thecurrent disclosure.

While various embodiments usable within the scope of the presentdisclosure have been described with emphasis, it should be understoodthat within the scope of the appended claims, the present invention canbe practiced other than as specifically described herein.

What is claimed is:
 1. A ball member usable in a ball valve, the ballmember comprising: a first round segment; and a second round segment,wherein the round segments are offset from one another and integrallyjoined symmetrically to one another relative to an axis of rotation ofthe ball member, the ball member having a progressively changing radiuswith respect to the axis of rotation, the ball member having a boreextending therethrough transverse to the axis of rotation, the borehaving a longitudinal axis, wherein the ball member further comprises: afirst shoulder defined by a first surface area located between the firstand second round segments, wherein the first round segment extends pastthe second round segment; and a second shoulder defined by a secondsurface area located between the first and second round segments,wherein the second round segment extends past the first round segment,wherein the bore comprises a first opening and a second opening, whereinthe first shoulder encircles part of the first opening of the bore, andwherein the second shoulder encircles part of the second opening of thebore, wherein the ball valve is opened and closed to fluid flow byrotating the ball member about the axis of rotation, and whereinrotation of the ball member progressively changes force of contactbetween the ball member and a ball valve seat.
 2. The ball member ofclaim 1, wherein the first and second round segments are offset from oneanother along the longitudinal axis of the bore.
 3. The ball member ofclaim 1, wherein the first round segment comprises a first center point,wherein the second round segment comprises a second center point, andwherein the first center point and the second center point arepositioned along the longitudinal axis of the bore.
 4. The ball memberof claim 1, further comprising: a first protruding member extending fromthe first and the second round segments along the axis of rotation; anda second protruding member extending from the first and the second roundsegments along the axis of rotation opposite the first protrudingmember.
 5. The ball member of claim 4, wherein the first protrudingmember or the second protruding member is integrally formed with thefirst and the second round segments.
 6. The ball member of claim 1,wherein a portion of the first round segment adjacent to a first openingof the bore comprises a symmetrical configuration with respect to thelongitudinal axis of the bore, and wherein a portion of the second roundsegment adjacent to a second opening of the bore comprises a symmetricalconfiguration with respect to the longitudinal axis of the bore.
 7. Theball member of claim 1, wherein the first shoulder encirclesapproximately half of the first opening of the bore, wherein the secondshoulder encircles approximately half of the second opening of the bore.8. The ball member of claim 1, wherein the ball member furthercomprises: a first border located between the first and second roundsegments; and a second border located between the first and second roundsegments opposite the first border, wherein the first and second bordersare located on the surface of the ball member, and wherein the first andsecond borders extend around the bore, wherein the first and secondborders extend generally perpendicularly with respect to thelongitudinal axis of the bore.
 9. The ball member of claim 1, whereinthe first round segment comprises a first curved surface having a firstinwardly curved edge and a first outwardly curved edge, wherein thesecond round segment comprises a second curved surface having a secondinwardly curved edge and a second outwardly curved edge, wherein thefirst outwardly curved edge coincides with the second inwardly curvededge, wherein the second outwardly curved edge coincides with the firstinwardly curved edge.
 10. A ball member usable in a ball valve, the ballmember comprising: a first partial sphere having a first surface and afirst center of a sphere; a second partial sphere having a secondsurface and a second center of a sphere, wherein the first and secondpartial spheres are integrated with one another forming the ball memberhaving a generally spherical outer shape, and wherein the first centerof the sphere and the second center of the sphere are located a distancefrom one another; a first shoulder defined by a portion of the firstpartial sphere extending past the second partial sphere; a secondshoulder defined by a portion of the second partial sphere extendingpast the first partial sphere, wherein the first shoulder encircles asubstantial part of the first end of the bore, and wherein the secondshoulder encircles a substantial part of the second end of the bore; anda bore having a first end, a second end, and a longitudinal axis,wherein the bore extends through the ball member transverse to an axisof rotation of the ball member, wherein the ball valve is opened andclosed to fluid flow by rotating the ball member about the axis ofrotation.
 11. The ball member of claim 10, wherein the first center ofthe sphere and the second center of the sphere are located at a distancefrom one another along the longitudinal axis of the bore on either sideof the axis of rotation.
 12. The ball member of claim 10, wherein aportion of the first surface located adjacent to the first end of thebore comprises a symmetrical configuration with respect to thelongitudinal axis of the bore, wherein a portion of the second surfacelocated adjacent to the second end of the bore comprises a symmetricalconfiguration with respect to the longitudinal axis of the bore.
 13. Theball member of claim 10, the ball member further comprising: the firstshoulder defined by an area between the first and second surfaces; andthe second shoulder defined by an area between the first and secondsurfaces opposite the first shoulder, wherein the first and secondshoulders extend around the bore, wherein the first and second shouldersextend generally perpendicularly relative to the longitudinal axis ofthe bore.
 14. The ball member of claim 10, wherein the first surfacecomprises a first inwardly curving and a first outwardly curvingboundary, wherein the second surface comprises a second inwardly curvingand a second outwardly curving boundary, wherein the first outwardlycurving boundary coincides with the second inwardly curving boundary,wherein the second outwardly curving boundary coincides with the firstinwardly curving boundary.
 15. The ball member of claim 10, wherein thefirst shoulder encircles approximately half of the first end of thebore, wherein the second shoulder encircles approximately half of thesecond end of the bore.
 16. The ball member of claim 10, furthercomprising: a first trunnion member extending from the ball member alongthe axis of rotation on the first side of the ball member; or a secondtrunnion member extending from the ball member along the axis ofrotation on the second side of the ball member; or a combinationthereof.
 17. A ball member usable in a ball valve, the ball membercomprising: a body segment having a generally rounded shape and an axisof rotation, wherein the body segment comprises: a bore having alongitudinal axis, wherein the bore extends through the body segmenttransverse to the axis of rotation; a first sloped surface; and a secondsloped surface, wherein the first and second sloped surfaces comprise aprogressively changing radius with respect to the axis of rotation; afirst shoulder defined by an area located between the first and secondsloped surfaces, wherein the first sloped surface extends past thesecond sloped surface; and a second shoulder defined by an area locatedbetween the first and second sloped surfaces, wherein the second slopedsurface extends past the first sloped surface, wherein the first andsecond shoulders are oriented generally parallel relative to each other,and wherein the ball valve is opened and closed to fluid flow byrotating the body segment about the axis of rotation.
 18. The ballmember of claim 17, further comprising at least one of: a firstprotruding member extending from the body segment along the axis ofrotation; and a second protruding member extending from the body segmentalong the axis of rotation, opposite the first protruding member. 19.The ball member of claim 18, wherein the at least one of the firstprotruding member and the second protruding member is integrally formedwith the body segment.
 20. The ball member of claim 17, furthercomprising: wherein the bore comprises a first rim and a second rim,wherein the first shoulder encircles part of the first rim of the bore,and wherein the second shoulder encircles part of the second rim of thebore.
 21. The ball member of claim 17, further comprising: the firstshoulder located between the first and second sloped surfaces; and thesecond shoulder located between the first and second sloped surfacesopposite the first shoulder, wherein the first and second shouldersextend around the bore, wherein the first and second shoulders extendgenerally perpendicular relative to the longitudinal axis of the bore.22. The ball member of claim 17, further comprising: the first shoulderlocated between the first and second sloped surfaces on one side of theball member; and the second shoulder located between the first andsecond sloped surfaces on opposite side of the ball member, wherein thebore comprises a first rim and a second rim, wherein the first shoulderextends generally parallel relative to the first rim, and wherein thesecond shoulder extends generally parallel relative to the second rim.23. The ball member of claim 17, wherein each of the first and secondsloped surfaces comprise inwardly curving and outwardly curvingboundaries adjacent to an opening of the bore, wherein a first outwardlycurving boundary coincides with a second inwardly curving boundary,wherein a second outwardly curving boundary coincides with a firstinwardly curving boundary.
 24. The ball member of claim 17, wherein thefirst shoulder encircles about half of the first rim of the bore,wherein the second shoulder encircles about half of the second rim ofthe bore.